EP0074734B2 - Betätigung für Bremsen od. dergl. - Google Patents

Betätigung für Bremsen od. dergl. Download PDF

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Publication number
EP0074734B2
EP0074734B2 EP19820304448 EP82304448A EP0074734B2 EP 0074734 B2 EP0074734 B2 EP 0074734B2 EP 19820304448 EP19820304448 EP 19820304448 EP 82304448 A EP82304448 A EP 82304448A EP 0074734 B2 EP0074734 B2 EP 0074734B2
Authority
EP
European Patent Office
Prior art keywords
piston
actuator
pawl
brake
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP19820304448
Other languages
English (en)
French (fr)
Other versions
EP0074734A2 (de
EP0074734A3 (en
EP0074734B1 (de
Inventor
Hugh Kenvyn Davies
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Honeywell UK Ltd
Original Assignee
Bendix Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Application filed by Bendix Ltd filed Critical Bendix Ltd
Publication of EP0074734A2 publication Critical patent/EP0074734A2/de
Publication of EP0074734A3 publication Critical patent/EP0074734A3/en
Application granted granted Critical
Publication of EP0074734B1 publication Critical patent/EP0074734B1/de
Publication of EP0074734B2 publication Critical patent/EP0074734B2/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/54—Slack adjusters mechanical self-acting in one direction for adjusting excessive play by means of direct linear adjustment
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
    • B60T13/12—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid
    • B60T13/22—Brakes applied by springs or weights and released hydraulically
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T17/00—Component parts, details, or accessories of power brake systems not covered by groups B60T8/00, B60T13/00 or B60T15/00, or presenting other characteristic features
    • B60T17/08—Brake cylinders other than ultimate actuators
    • B60T17/083—Combination of service brake actuators with spring loaded brake actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/02—Fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/02—Fluid pressure
    • F16D2121/12—Fluid pressure for releasing a normally applied brake, the type of actuator being irrelevant or not provided for in groups F16D2121/04 - F16D2121/10
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2123/00—Multiple operation forces

Definitions

  • This invention relates to actuator devices for brakes or the like and relates in particular to an actuator capable of operation by one of two control signal pressures one of which is for spring actuation.
  • a combined service and parking hydraulic brake system wherein the combined parking and service actuator comprises a pair of pistons in a cylinder.
  • One of the pistons is connected to a force output member and is acted upon by the force of a spring between it and the further piston.
  • the parking brake force is released by applying fluid under pressure to the first mentioned piston acting against the spring and service braking is applied by fluid under pressure acting on the second piston.
  • Brake slack is adjusted by ratchet means acting between the cylinder and the second piston. Therefore only relatively small stroke of the spring is necessary.
  • One object of the invention is to provide an actuator for brakes or the like in which it is possible to minimise in a simple manner the stroke of the spring- operated portion without the necessity of having a service brake piston of large effective area.
  • the first pressure responsive member may be arranged to contain the second pressure responsive member or alternatively the first and second pressure responsive members may be movable one relative to the other within a common cylinder.
  • FIG. 1 shows a cylindrical housing 1 provided at one end with a first control pressure input port 2 and being enclosed at the other end by an end plate 3.
  • the end plate includes a ratchet mechanism denoted generally by the reference 4 operable in conjunction with ratchet teeth 5 provided on a tubular force output member 6.
  • the cylindrical housing has a first pressure responsive member formed by a piston 7 and associated parts sealingly slideable in the cylindrical bore with a piston seal 8.
  • the piston 7 has a screw threaded skirt 9 threaded into a further skirt 10 of a cylindrical part 11 which itself is integral with the output member 6 and carries a further seal 20 sealingly slideable in the cylinder.
  • the part 10 is itself internally cylindrical and slideable therein there is a second pressure responsive member in the form of a piston 12 having a piston rod 13 extending outwardly of the device through the force output member 6 acting on a pad member 14.
  • This pressure is derivable from a second input port communicating via a channel 18 through a number of passages such as 19, seals being provided at 20, 21 and 22.
  • first pressure responsive member 7 is a relatively long stroke pressure responsive member operable to produce a direct outputforce via the force output member 6 acting on the pad member 14 for applying a brake.
  • the pressure responsive member 12 however is relatively short stroke pressure responsive member acting between the force output member 6 and the pad 14 to apply the brake.
  • the chamber 16 is assumed to be fully pressurised with sufficient air pressure to hold the spring means 15 in the compressed condition and if in addition a control pressure is applied at the first control port 2, the first pressure responsive piston 7 is urged in a direction to drive the force output member 6 outwardly of the housing 1. If the clearance on the brake pads or shoes is such that the forward stroke is greater than the distance between the flank of one ratchet tooth 5 and the flank of the next tooth, plus any necessaryy override or backlash, the ratchet means 4 will pass over at least one such tooth before the full brake force is applied.
  • the force output member Upon subsequent release of air from the port 2, the force output member is permitted to return only by a maximum distance corresponding to the distance between the flank of one ratchet tooth and the flank of the next ratchet tooth plus any necessary override and subsequent backlash.
  • the application of the spring brake can be effected by release of fluid pressure from the chambe 16 via the second control pressure port.
  • the second pressure responsive piston 12 is thereby moved forward by spring means 15 together with the pressure responsive member 7. Since the output member has been locked into a position corresponding to no more than a predetermined return stroke, the second pressure responsive member 12 requires only to move a short distance corresponding to the said return stroke in order to apply the brake by acting between the force output member and the brake itsef.
  • hold-off pressure is reapplied via the second signal pressure control port to the chambe 16 and the piston 12 returns to the illustrated position with the spring means 15 fully compressed.
  • a spring brake portion may be employed with a rod passing through the tubular member and which is of only relatively short stroke.
  • Fig. 2 this shows an arrangement which is in many ways similar to the arrangement of Fig. 1 to the extent that is equally provides a convenient arrangement with a relatively long stroke service brake actuator and a relatively short stroke spring or secondary brake actuator contained therein.
  • the cylinder housing 1 and the end plate 3 together with ratchet means 4 may be substantially identical with the arrangement of Fig. 1. It is seen however that the first pressure responsive member now has a portion 31 with piston seal 49 and which is provided with a tubular piston rod 32 the outward end of which is screwed at 33 into the force output member 34 which again is provided with ratchet teeth 35.
  • Member 34 also has an integrally moveable wall 47 with a seal 50.
  • a second pressure responsive member in the form of a piston 36 which is sealingly slideable also in the same bore 37 of the cylindrical housing.
  • the second pressure responsive member 36 is provided with a piston rod 38 which is slideable within the tubular piston rod 32 and is dowelled to the piston 36 by a dowel 39 extending through a short slot 40 in the tubular member 32 a shown.
  • spring means in the form of Belleville washers 41 or the like is provided between the pistons 31 and 36 and in the position shown, these are shown under compression by virtue of the presence of controlling fluid pressure applied via a second port 46 to the chamber 42 acting on the pressure responsive member 36, further seals being provided at 43, 44 and 45 as shown.
  • the pressure in the chamber 42 is reduced via the second control pressure port with the effect that the spring means 41 act between the first pressure responsive member 31 through the piston 36, the dowel 39, the inner piston rod 38 and the brake. Subsequent recovery of full pressure in the chamber 42 causes return movement of piston 36 to again release the brake.
  • pawl and ratchet mechanism employed in end plate 3 of the actuator devices of Fig. 1 or Fig. 2, this is shown in more detail in Figs 3 and 4.
  • the ratchet mechanism 4 and teeth 5 of Fig. 1 or Fig. 2 are seen to be required to support the full force exerted by the spring brake portion of the actuator.
  • each ratchet tooth 5 is substantially perpendicular to the axis and engaging with the pawl 4 which is spring loaded by a spring 68 and a ball 67 and also pivoted as discussed below so that it rotates clockwise and lifts when the push rod moves to engage the oblique flank of the next tooth with the pawl but is restrained against rotation when the push rod moves in the opposite direction to engage a perpendicular flank.
  • the pawl is arranged to provide a substantial backlash in its operation.
  • the pawl is pivoted as shown in Fig. 4 on two co-axial cylindrical extensions 56 and 57 which are borne in bearings 58, 59 and 60. These are radially located in bores 61 and 62 by resilient mounting rings 76. These are shown as 'O' rings but could be rings of any cross section and of any resiliently deformable material.
  • the back face 63 of the pawl 4 forms part of a cylinder co-axial with cylindrical extensions 56 and 57.
  • the diameters of the cylindrical extensions of pawl 4, bearings 58, 59 and 60 and of bores 61 and 62 are arranged such that the clearance 64 is small in comparison with the clearances 65 and 66 which are shown exaggerated for clarity.
  • the pawl may be released from the ratchet to per- met the push rod to be retracted, by striking a cylindrical extension 56 on the end 71, thus moving pawl 4 and bearing 59 axially against spring 72 until bearing 59 butts against bearing 60 atwhich point the pawl 4 will be clear of ratchet teeth.
  • This axial movement may be effected by other means, e.g., a cam (operated manually or otherwise) or a screw actuator or a fluid operated actuator.
  • the reaction force on the member 6 causes movement of that item in the release direction until the force applied through that push rod is released.
  • the pawl may be held out of engagement with the ratchet teeth either manually or by other means until the required retraction is effected.
  • the rearface 73 of pawl 4 may be chamfered toward the engaging face 74 and the oblique face of each tooth to be chamfered toward the engaging end 75 so that a lead-in is provided and engagement is effected whatever the relative positions of the two parts albeit that in some cases the pawl returns to the rotated and raised position.
  • Afurther refinement applicable to a fluid pressure operable service and spring applied parking dis brake actuator is for the spring 72 to be of insufficient strength to re-engage the pawl, but merely of sufficient strength to enable bearing 59 to follow the pawl as it is pushed into engagement.
  • Afluid pressure cylinder may be used to move the pawl into engagement with the ratchet, the fluid being in connection with and at the same pressure as that compressing the brake application spring. This resists any attempt to disengage the pawl unless pressure was released from the spring compression chamber either deliberately or due to leakage.
  • FIG. 5 One embodiment of such an arrangement is shown diagrammatically in section in Fig. 5 wherein the cylindrical extension 57 of pawl 4 in Fig. 4 is shortened to that shown as 131, and runs in bearing 132 (in place of 59 and 60) located in a piston 133 by a resilient ring 34.
  • Pistonchamber 135 is at the same pressure as, and in communication with the spring compression chamber (16 or 42), via passages 137 and 139 formed in the housing. These chambers are thus supplied with fluid pressure conveying fluid from the spring brake system at a pressure determined by a spring brake control valve.
  • a screwed plug 141 provides the end of the cylinder 135 and acts as a stop for piston 133 and carries a seal 142 against loss of fluid or fluid pressure. Access to piston 133 and seal 143 for inspection and maintenance is effected by removal of pluf 141.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Braking Arrangements (AREA)

Claims (10)

1. Betätigung für Bremsen oder dergleichen, umfassend ein Gehäuse (1) mit einer zylindrischen Bohrung, einer ersten Drucksignaleingangsöffnung (2), einer zweiten Drucksignaleingangsöffnung (18;46), einen auf Fluiddruck ansprechenden ersten Kolben (7,10,11;37,47), der in der Bohrung betätigbar ist beim Ansprechen auf ein Fluiddrucksignal an der ersten Signaleingangsöffnung (2), um einen Vorwärtshub auszuführen und eine Ausgangskraft an ein Bremselement (14) oder dergleichen anzulegen, eine automatische Nachstelleinrichtung (4,5;4,35), die in Relation zu dem ersten Kolben betätigbar ist für dessen Festlegen relativ zu dem Gehäuse (1) gegen mehr als einen vorbestimmten Rückkehrhub, und mit einer mittels Federkraft angelegten und mittels Fluiddruck gelösten Parkbremseinrichtung oder dergleichen (12,15;36,41), die eine unter Druckstehende Feder (15;41) zwischen dem ersten Kolben und einem zweiten Kolben (12;36) aufweist, der auf einen Fluidsteuerdruck an der zweiten Signaleingangsöffnung (18;46) anspricht und über eine Kolbenstange (13;48) zwischen dem ersten Kolben (7,10,11;31,47) und dem Bremselement (14) wirkt, um die bremse oder dergleichen anzulegen, dadurch gekennzeichnet , daß der erste Kolben mit einem rohrförmigen Ausgangsteil (6;34) versehen ist, der Mittel zum Bewirken des Festlegens relativ zu dem Gehäuse hat, die Kolbenstange (13;48) durch den rohrförmigen Ausgangsteil (6;34) hinduch axial bewegbar ist, und daß der erste Kolben (7,10,11;31,47) wenigstens zwei Dichtungen (20,21,22;45,50) hat, welche den Steuerfluiddruck an der zweiten Öffnung (18;46) des Gehäuses in Verbindung mit einem Raum (16,42) zwischen einem Teil (11;47) des ersten Kolbens und des zweiten Kolbens (12;36) abdichten, um in einer Vorwärtsrichtung auf den genannten Teil des ersten Kolbens und in Rückwärtsrichtung auf den zweiten Kolben (12;36) zu wirken, wodurch der Druck an der zweiten Öffnung keine Nettokraft auf den ersten Kolben in Rückwärtsrichtung ausübt.
2. Betätigung nach Anspruch 1, dadurch gekennzeichnet, daß der erste Kolben (7,10,11;31,47) den zweiten Kolben (12,36) mit sich trägt.
3. Betätigung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der zweite Kolben (12) in einer Zylinderbohrung abgedichtet verschiebbar ist, die in dem ersten Kolben (7,10,11) gebildet ist.
4. Betätigung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der zweite Kolben (36) mit seiner Dichtung (43) in der gleichen Bohrung (37) wie der erste Kolben (31,47) abged ichtet versch iebbar ist.
5. Betätigung nach Anspruch 4, dadurch gekennzeichnet, daß der zweite Kolben mit der Kolbenstange (48) über eine Querverbindungseinrichtung (39) verbunden ist.
6. Betätigung nach irgendeinem der vorhergehendenAnsprüche, dadurch gekennzeichnet, daßdie Nachstelleinrichtung (4,5) eine Klinke (4) und ein Gesperre (5) aufweist und die Klinke federnd angebracht ist, um massiven Eingriff unter Last mit einem Gehäuseteil (3) zu schaffen.
7. Betätigung nach Anspruch 6, dadurch gekennzeichnet, daß die Klinke (4) durch einen außen vorragenden Teil (121) von Hand lösbar ist.
8. Betätigung nach Anspruch 7, dadurch gekennzeichnet, daß die Klinke (4) einen zugeordneten auf Arbeitsmitteldruck ansprechenden Teil (133) hat, der betätigbar ist, um einer Freigabe von Hand entgegen zu wirken.
9. Betätigung nach Anspruch 7 oder 8, dadurch gekennzeichnet, daß die Klinke (4) entlang ihrer Drehachse für Zwecke ihres Freigebens bewegbar ist.
10. Betätigung nach Anspruch 9, dadurch gekennzeichnet, daß die Klinke (4) angefast ist, um eine Einführung für Wiedereingriff mit den Gesperrezähnen (5) zu schaffen.
EP19820304448 1981-09-09 1982-08-24 Betätigung für Bremsen od. dergl. Expired EP0074734B2 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB8127307 1981-09-09
GB8127307 1981-09-09

Publications (4)

Publication Number Publication Date
EP0074734A2 EP0074734A2 (de) 1983-03-23
EP0074734A3 EP0074734A3 (en) 1983-05-04
EP0074734B1 EP0074734B1 (de) 1986-12-10
EP0074734B2 true EP0074734B2 (de) 1992-06-17

Family

ID=10524411

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19820304448 Expired EP0074734B2 (de) 1981-09-09 1982-08-24 Betätigung für Bremsen od. dergl.

Country Status (2)

Country Link
EP (1) EP0074734B2 (de)
DE (1) DE3274673D1 (de)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2599101A1 (fr) * 1986-05-23 1987-11-27 Muller Alfred Freins de stationnement automatiques
FR2656906A1 (fr) * 1990-01-05 1991-07-12 Renault Vehicules Ind Frein multidisque a commande par fluide avec dispositif compensateur d'usure pour vehicules industriels.
DE4445960C1 (de) * 1994-12-22 1996-07-11 Grau Gmbh Bremszylinder für eine druckluftbetätigte Fahrzeugbremse
FR2808062B1 (fr) * 2000-04-19 2002-08-23 Sime Ind Frein a disque, en particulier pour usage industriel
EP4059792B1 (de) * 2021-03-15 2024-03-27 ZF CV Systems Europe BV Federbremsaktuator zur verwendung in einem fahrzeug und verwendung einer tellerfeder darin

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR779359A (fr) * 1933-12-27 1935-04-03 Freins Jourdain Monneret Dispositif de rattrapage de jeu pour freins hydrauliques
FR1197976A (fr) * 1957-03-05 1959-12-03 Magneti Marelli Spa Perfectionnements aux cylindres à double alimentation pour la commande d'installations de freinage pneumatique
GB839604A (en) * 1957-06-03 1960-06-29 Bendix Westinghouse Automotive Automatically adjusted fluid pressure actuator
US3158069A (en) * 1962-04-06 1964-11-24 Wagner Electric Corp Brake operating mechanism
FR1387663A (fr) * 1963-04-06 1965-01-29 Magneti Marelli Spa Dispositif à double effet, pour la commande de freins par un fluide sous pression
US3759147A (en) * 1971-02-24 1973-09-18 Certain Teed St Gobain Diaphragm brake actuator
US3677607A (en) * 1971-04-05 1972-07-18 Harold B Schultz Hydraulic power brake system
US3908804A (en) * 1974-07-11 1975-09-30 Caterpillar Tractor Co Service and parking brake actuation piston with adjuster mechanism
DE2508771C2 (de) * 1975-02-28 1982-11-25 Wabco Fahrzeugbremsen Gmbh, 3000 Hannover Selbsttätige Nachstellvorrichtung für Scheibenbremsen
DE2650490C2 (de) * 1976-11-04 1986-06-05 Wabco Westinghouse Fahrzeugbremsen GmbH, 3000 Hannover Pneumatisch oder hydraulisch gesteuerte Scheibenbremse
SE399393B (sv) * 1976-11-15 1978-02-13 Sab Ind Ab Bromsaktuator
DE2718765A1 (de) * 1977-04-27 1978-11-02 Knorr Bremse Gmbh Scheibenbremse fuer fahrzeuge, insbesondere strassenfahrzeuge

Also Published As

Publication number Publication date
EP0074734A2 (de) 1983-03-23
DE3274673D1 (en) 1987-01-22
EP0074734A3 (en) 1983-05-04
EP0074734B1 (de) 1986-12-10

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